Milling machine transmission control mechanism



6 Sheets-Sheet l INVENTORS.

RICHARD K. LEBLUND AND HARRY C. KE'MPER ATTORNEY.

D 1952 R. K. 1.1 :BLOND ETAL MILLING MACHINE TRANSMISSION CONTROL MECHANISM Original Filed June 16, 1950 April 1, 1952 R. K. LE BLOND ETAL 2,591,268

MILLING MACHINE TRANSMISSION CONTROL MECHANI ISM Original Filed June 16', 1950 6 Sheets$heet 2 IN VEN TORS.

RICHARD A. LEBLOND AND HARRY C. KEMPER MAM ATTORNEX Aubryil'w'l; T952 R. K. LE BLOND ET AL MILLING MACHINE TRAI ISMISSION CONTROL MECHANISM Original Filed June 16, 1950 6 sheets-sh et :5

INVENTORS RIM-MR9 If. LEELOIVU BY MDHARWV C. KEMPEW A r TOW/VEW Ap 1, 1952/ R. K. LE BLOND ETAL' 2,591,268

MILLING MACHINE TRANSMISSION CONTROL MECHANISM Original Filed June 16, 1950 6 Sheets-Sheet 4 INVENTORS. RICHARD K. LEBLCWU BY Mn MAI-Pm C. KEMFEW April 1, 1952 R. K. LE BLOND ETAL 2,591,268

MILLING MACHINE TRANSMISSION CONTROL MECHANISM Original Filed June 16, 1950 6 Sheets-Sheet 5 INVENTORS.

RICHARD K. LEELOND AND HARRY C. KEMPER- Arron/var.

April 1, 1952 I R. K. LE BLOND' ET AL MILLING MACHINE TRANSMISSION CONTROL MECHANISM Original Filed June 16, 1950 6 Sheets-Sheet 6 N T \O l l I l m r r i f i :i d J Q 2 a on m 2 m nd 24% S2 S2 7 "'i? no a 8 E: 55 52 I O 3g :7 2

( X g u 7 o ((5; 6 :3 m :z a Q 3 N h w" ul 9 E g a D '5 T LL 5- n n SL2 INVENTORS.

P/CHARO K. LEBLOND AND HARRY C. KEMPER ATTORNEY.

Patented Apr. 1, 1952 MILLING MACHINE TRANSMISSION CONTROL MECHANISM Richard Knight Le Blond, Cincinnati, and Harry G. Kemper, Goshen Township,

Clermont County, Ohio, assignors to The R. K. Le Blond Machine Tool Company, Cincinnati, Ohio, a

corporation of Delaware Original application June 16, 1950, Serial No. 168,462. Divided and this application April 24, 1951, Serial No. 222,696

iClaims. (Cl. 74-337.5)

This invention pertains generally to transmission and control mechanism for milling machines, and is more particularly directed to such mechanism as utilized for actuating the knee, saddle and table movements of the milling machine.

This is a divisional application of original application, Serial No. 168,462, filed June 16, 1950, now Patent No. 2,580,307 issued December 25, 1951.

Another object of this invention is to provide an improved single handle control mechanism for selectively operating the feed drive transmission of a milling machine.

And still another object of this invention is to provide specific improvements in a change feed transmission and control for the feed drive of a milling machine knee, saddle and table which is economical to manufacture and highly accurate and quiet in operation while at the same time requiring a minimum of space.

It is also an object of this invention to provide certain improvements in the control mechanism for a sliding gear change feed transmission for a milling machine to improve the performance of the machine and reduce the cost and time required in its manufacture.

' Further features and advantages of this invention will appear from a detailed description j'of the drawings in which:

1 Figure 1 is a right hand side elevation of a milling machine knee incorporating the features of this invention.

Figure 2 is a front elevation of the milling machine knee shown in Fig. 1.

Figure 3 is a left hand side elevational view of the knee shown in Figure 1.

Figure 4 is a sectional view through th knee of the line l--4 of Figures 1, 3, and 5.

Figure 5 is a diagramatic extended sectional view onthe line 5-5 of Figure 4.

Figure 6 is a section on the line 5-5 of Figure 2.

Figure '7 is a sectional view on the line 1-1 in Figures 2, 3, and 4.

For illustrative purposes this invention is shown applied to a typical universal milling machine having a column l0 having guide ways 1! upon which is slidably mounted th knee I2 for vertical reciprocation. On top of the knee is carried the saddle I3 on top of which is the usual swivel base 14 which carries the work table 15 on suitable guide ways 15.

The knee, saddle and table are reciprocated in their respective move- The shaft 11 is connected through a suitable universal joint 18 which in turn is connected to the input drive shaft 19 of the feed change transmission, the shaft 13 being journaled on suitable bearings 20 in the knee 12.

The feed drive power take off from the shaft I9 is transmitted from the gear 21 fixed to the shaft 19 to the gear 22 fixed on the shaft 23 journaled in suitable bearings 24 in the feed box housing 25, this housing being formed with a flanged outer portion 26 which is secured to the knee !2 by suitable bolts 21. Axially slidable on the spline portion 28 of the shaft 23 are two double gears 29 and 33 which are secured together by suitable means such as welding orthe like at 31. The double gear 29 comprises the small gear 32 and the larger gear 33 while'the double gear 30 comprises the smaller gear 34 and the larger gear 35. The assembly of gears just described are free to shift axially of the shaft 23 on the spline portion 28 thereof so that the gear 34 engages the gear 36a of the double gear 36 fixed to the shaft 31 journaled on suitable bearings 38 in the feed box housing 25. The gear 35 is adapted to slide into an engagement with the gear 33 of the double gear 36. Similarly, gear 32 is adapted to slide into driving engagement with the gear 40 of the double gear 4| fixed to the shaft 31 while the gear 33 is arranged to engage the gear 42 of the double gear 4L. By this arrangement sliding the double gears 29,-3i1 on the shaft 23 to four selected positions, four different speeds of rotation arev provided for the shaft 31.

Power take off from the shaft 31 is derived from the gear 39 which constantly drives a gear 43 fixed to the shaft 44 journaled on suitable'bearlugs 45 in the feed box housing 25. Also fixed on the shaft 44 is a wide face pinion 43 which is adapted to be slidingly engaged by the gear 41 of the double gear 48 slidably mounted on the spline portion 49 of a shaft 50 journaled in suitable bearings 5! in the feed box housing 25. The double gear 43 also has a gear 52 which may be slid into engagement with the gear 43 fixed to the shaft 44. The gear may also enage a gear 53 formed on the double gear 54 which is fixed to the shaft 55 jour'naled in suitable bearings 56 in the feed box housing 25. Also formed on the double gear 54 is a wide faced gear 51 which meshes with the gear 41 of the double gear 48 on the shaft 50. Thus between the shafts 44--5ll--55 are 3 selectable gearratios provided by sliding the double gear 48 on the shaft 53 as follows: I

The drive from gears 35-4151; the drive through gears 46-41 and 5253; and the drive from gear 4352 and gears 41-51. Thus 3 speed ratio changes are effected between the shafts 44 and 55.

Further feed reduction drive is obtained between the shaft 55 and the output shaft 53 journaled in suitable bearings 59 in the feed box housing 25. This comprises a double gear to journaled on the bearing portion iii of the shaft 50, the double gear 50 comprising. a large gear 62 which is driven from a pinion t3 fixed to the shaft 55. A smaller gear 64 of the double gear so drives the large gear 65 of the double gear 66 journaled on the bearing portion 61 of the shaft 55. The gear 53 formed on the double gear 65 drives a gear 59 fixed on the shaft 58 to thereby bring the final drive out from the feed box 25 to the shaft 58.

Power output from the shaft 53 of the feed box 25 is transmitted through an overrunning clutch Ill to the gear H which is fixed on a shaft 12 iournaled in suitable bearings 13a, Hid, and 15a. in the knee [2 of the milling machine, the

gear TI being driven by the outside gear 53 of derived from a gear I4 journaled on the shaft I9, which is constantly in mesh with the elongated gear' I suitably fixed to the shaft 72. The gear I4 may be connected to or released from drivin relationship on the shaft 19 by means of a suitable multiple disk clutch which is actuated by the usual shifter spool 77 in a well known manner. Thus whenever the clutch I8 is engaged direct rapid driving power from the shaft I9 is immediately transmitted to the elongated gear. I5on the shaft 12 to affect rapid rotation of the shaft I2 while at the same time the overrunning clutch allows the gear I3 to rotate vmore rapidly than the shaft 58 even though the feed drive is continuing at a much slower rate to the shaft 58 from the shaft I3. As soon asthe multiple disk rapid traverse clutch i6 is disengagedthe feed driving power as described immediately picks up through the overrunning clutch I0 to apply the feed drive to the shaft 12 through the gear? as described. 7

The knee !2 of the milling machine is reciprocated in vertical movement at feed and rapid traverse rates by shifting the reversing clutch member 18 to engage either one or the other of the bevel pinions I9 and Bi) 'journaled on the shaft 12 as best seen in Figure 6. Each of the bevel pinions "I9 and 80 are in constant engagement with the bevel gear SI fixed to the elevating screw 82 to effect raising and lowering of the knee of the milling machine in the well known manner. 7 V

The saddle I3 is reciprocated in horizontal in and out movement by power from the shaft I2 which is connected through the gear H to a gear 83 journaled on the saddle cross feed screw 84 and held against axial movement in the bearing 85 carried in the knee I2. A reversing gear train comprising the gear 85 fixed on the shaft I2 drives an idler pinion ll'l journaled on a suitable hearin 88 on the shaft 89 rigidly held-in the knee 12. The idler 81 in turn drives the gear 99 journaled against axial movement on a suitable bearing 9| around the cross feed screw 8.4. Aclutch spool 92 having clutch teeth 93 and 84 respectively engage the clutch teeth 55 and 96 of the gears 83 and to so as to affect a reversal drive of the screw 84 in one direction or the other or a neutral position of non-drive to the screw 84. The cross feed screw 84 is connectedthrough suitable nut mechanism not 6o 7, the feed change gearbox 25 has a single lever 'of the clutch spool TI.

shown to actuate the saddle in a well known manner. The cross feed screw may also be rotated manually by means of a suitable hand wheel 9! connected to the outer end of the shaft 34.

The drive for actuating the work table I5 is derived from the gear l5 which drives a gear 98 fixed on the bevel pinion sleeve 99 journaled in a suitable bearing I carried in the downwardly extending bracket IilI which in turn is supported on the swivel base It of the milling machine.

The pinion sleeve 59 has a bevel pinion I02 formed thereon which in turn drives a bevel gear H33 fixed to the vertical shaft I64 which in turn has a bevel gear H25 in engagement with a pair of mating bevel gears similar to the gear 29 and 86 already discussed in connection with the knee elevating mechanism. A suitable clutch device indicated at 96 connects the bevel pinion Ill? to apply the drive to the table feed screw IE8 in a well known manner. A suitable trip and control lever its connected through suitable linkage mechanism at! I0 through the Eever III .pivotally mounted on the pin H2 fixed to the swivel base I4 and having the forked ends H3 serve to control the trip clutch for the work table I5 in a conventional manner.

The control of the rapid traverse to the knee, saddle and table is afiected by means of" the control lever II4 mounted on arock shaft H5 journaled in a suitable bearing H6 in the knee I2 of the milling machine. The inner end of the rock shaft H5 has fixed to it a shifter yoke I I? by means of the pin H8 and has end portions H9 which engage in the annular slot Moving the control lever upwardly from position Il la to position II4b causes the clutch it to be engaged to apply'the rapid traverse drive power as described. Release of the lever from the position II4b allows it to return to the position Ilsa to disconnect the rapid traverse driving power. The member to be actuated at rapid traverse or at feed is determined by the respective control levers, control lever I09 regulating the table movement, lever IZi controlling the cross feed or saddle movement and lever I22 controlling the vertical movements of the knee. Since the detail structure of these control levers form no part of this invention it is sufficient to state that the control lever I2I through suitable mechanism operates the clutch spool 92 described for connecting the drive power from the shaft '12 to the crossfeed screw 34 in one direction or the other. Also the control lever I22 operates the clutch spool 18 for engaging either the bevel pinion T9 and 86 as described to aifect the stoppage of one direction or the other drive to the elevating'screw 82 for the knee.

Referring more particularly to Figs. 4, 5, and

controldevice comprisin the lever or handle I23 which is carried on an axially slidable and rockable shaft I24 for simultaneously controlling the shiftable gears 29,30 and48 of the feed box for any desired selection of feed rate. 'The axially slidable and rockable shaft I24 is supported in a suitable. bearing H25 in thefeed box 25 and has fixed on its inner end by a pin I26 the shifter spool I21 having an annular slot !28 which is engaged by a pin I29 carried in the shifter yoke I38 which is axially slidable on the rod I3I rigidly supportedin the feed box 25, on suitable bearings I32 and I33 and held in place therein by means of the set screw I34. The shifter yoke I30 has a projecting arm I30a having a forked end to form a slot I35 which engages each of the side faces of the gear 41 of the double gear 48 so that axial movements of the handle I23 and shaft I24 to the positions I23a, I231), and I23c, shifts the gear 48 to its 3 selectable positions.

Rocking motion of the control lever I23 and shaft I24 causes shifting of the gear 29-30.

Slidably mounted on the bearing surface I36 of the shaft I24 is the cam drum I31 which is connected to be rotated by rocking of the shaft I24 through a suitable key I38 fixed to the shaft I24 but slidable in the key way I39 of the cam drum I31. The cam drum I31 is restricted against axial movement but allowed freedom of rotary movement by confinement between the abutment face I40 of the abutment pin I4I fixed in the feed box housing 25 and the end I42 of the abutment pin I43 slidably mounted in a suitable bore I44 in the feed box housing 25. A suitable adjustain an out to shift the gear 48 as described.

Around the periphery of the cam drum I31 is formed a helical cam slot I49 in which operates the pin I50 fixed in the outer end of the lever arm II which is secured to the rock shaft I52 supported in suitable bearings I53 and I54 in the feed box housing 25. of the rock shaft I52 has a lever arm I 55 secured The outer rearward end thereto and extending upwardly and terminating in a boss carrying a shifter piece I56 supported in a suitable journal bearing I51, the

member I56 engaging in the annular groove I58 of the shiftable gear 29-30. Thus, when rocking motion is imparted to the shaft I24 by twisting the control handle I23 the helical cam slot I49 causes the lever I5I and the lever I55 to shift the gear 29-30 to its respective four operative positions.

The in and out sliding movement of the shaft I 24 is limited by engagement of the face I59 with the face I48 of the cam drum I31 and by the face I 60 of the spool I21 engaging the face I41 of the cam drum I31. A suitable detent comprising a spring pressed plunger I6I operatingin detent notches I 62 formed in the shaft I3I provides means for readily positioning the shaft I24 in its three shiftable positions. The positioning of the control lever in rotary positions is accomplished by means of the segmental detent portion I63 formed integral with the lever I5I and having a series of four detent notches I64 which are engaged by the spring urged detent I55 carried in the feed box housing 25.

Formed on the control handle I23 is an indieating pointer I66 which cooperates with the U- shaped index plate I51 which has a series of four groups of three numbers indicated at I68, I 69, I10, and HI, as best shown in Figure 2. These four positions represent the four shiftable movements for the gear 29-30. The three concentric groupings of figures I12 represent the three in and out positions for the handle I23 and the gear 48.

Referring particularly to Figure 5 it is to be noted that in the arrangement of the feed. box gear train that there are never more than two gears combined in a double gear assembly The advantage of keeping the gear construction limited to groups of two gears in a double gear greatly facilitates the accuracy of the-heat treating operations and subsequent gear finishing work. It is also to be noted that the gears that are combined in the double gear set-ups are maintained in more nearly the same diameter and in no case is the very large gear combined closely with the very small gear in a double gear assembly. This further facilitates the'ma'nufacture and heat treating of the gears and provides a more effective and rigid transmission.

It is to be further noted that in the geararrangement shown for the combined double gears 29-30 on the shaft 23 that the largest gear 35 is located one position from the end of the four gear assembly so as to give an absolute minimum of space required for a progressive gear shift to four positions for the gear 29-30 and thereby reduce the overall length of the shafts in the feed box transmission 25 effecting greater rigidity and accuracy of performance .of the gear transmission.

It is to be further noted in connection with the three position shifting gear 48 on the shaft that there is obtained the action of a double back gear drive through the gear shift position 46-41 and 52-53 in one extreme position and a double speed up in the other position effected through the gearing 43-52 and 41-51 so as to afford a very large ratio of speed change between the shafts 44 and 55. It is also to be noted in connection with the gear 48 that in making any of the three changes that only one gear engagement is required, this being due to the wide faced gears 46 and 51 which always maintain at least one gear engagement while the other gear changes are being undertaken. This makes for greater ease in shifting of the feed box transmission and a more rapid and easy selection of the desired feed rate by the operator. '7

Still another feature of the construction of the feed box transmission is that all of the various bearings 24, 38, 45, 5|, 56 and 59 are identical and the respective supporting bores in the feed box housing 25 are also identical so as to facilitate the rapid'and economical machining of all the bored holes in the housing 25 with the same set of boring tools. This makes for greater accuracy of the center distances between the various shafts and an improvement in the quietness and efficiency of operation of the various geared trains.

It is to be further noted that a maximum ratio is provided through the feed change gear box 25 (in this exemplary disclosure 40 to 1) while at the same time the difference in ratio between any two gears is small in no case more than 2 /2 to 1, so as to maintain a good involute tooth action between each and every gear in the feed 1 box transmission, thus providing a smooth, quiet and steady flow of power to the machine tool.

It is to be further noted'that the entire feed ranges are effected by moving only two sliding gears, namely the gears 29-30 and the gear 43 from a commonsingle lever control I23 which may readily move the gears in proper sequential order to any desired feed rate as indicated on the index dial I61.

It is also to be noted that the feed or'speed increase for the transmission is effected by means of the control handle I23 which is pushed in and rotated to the right and in normal manner for effecting increases, and which is pulled. out and to decrease the feed or speed from the transmission. This greatly facilitates the quick and easy selection of change in feed and speed even without reference to specific values on the feed or speed change indicating dial E61.

It should also be noted in view of the above description that in shifting the two gears '29-3ll and 48 thatfeed and speed changes are obtained without shifting through a fast gear to get down to a slow rotating gear and vice versa. This makes for easy shifting and elimination of substantially all clash in making the various rate changes desired. I There has thus been provided an improved feed or speed change transmission mechanism for a milling machine or other machine tools having certain specific structural improvements over all former devices so as to provide a most efficient transmission mechanism both from the operative and manufacturing standpoints.

Having thus fully described this invention and its numerous attendant advantages, it is obvious that many changes may be made in the form, construction and arrangement of the parts without departing from the spirit or scope of the in vcntion or sacrifice its attendant advantages, the form herein described being a preferred embodiment for purposes of exemplifying this invention.

The invention is claimed as follows:

1. In a change speed transmission having, a transmission housing, a gear set, a pair of shiftable members in said gear set, a single lever con trol mechanism for shifting said members comprising, an axially slidable and rockable shaft carried inthe change speed transmission housing, a handle rigidly fixed on the outer end of said shaft, a shifter spool fixed on the inner end of said shaft engaging a shifter yoke movably mounted in said housing, means for connecting said yoke to a shiftable member in said transmis sion, a shifter cam drum located between said lever and said spool relatively axially slidable on and supported by said slidable and rockable shaft, means'carried by said housing for restricting axial movement of said cam drum relative to said housing while allowin rotary movement thereof by the rocking motion of said shiftable and rockable shaft, a cam track in said cam drum, shifting lever mechanism actuated from said cam track upon rocking rotation of said handle, and means for connecting said shifter lever mechanism to shifting members in said change speed transmission.

"2. In a change speed transmission having, a transmission housing, a gear set, a pair of shiftable'members in said gear set, a single lever control mechanism for shifting said members comprising, an axially slidable and rockable shaft carried in the change speed transmission housing, a handle rigidly fixed on the outer end of said shaft, a shifter spool fixed on the inner end of said shaft engaging a shifter yoke movably mounted in said housing, means for connecting said yoke to a shiftable member in said transmission, a shifter cam drum located between said lever and said spool relatively axially slidable on arid supported by said slidable and rockable shaft, means carried by said housing for restricting axial movement of said cam drum relative to said housing while allowing rotary movement thereof by the rocking motion of said shiftable and rockable shaft, a cam track in said cam drum, shifting lever mechanism actuated from said cam track upon rocking rotation of said '8 V handle, means for connecting said shifter lever mechanism to shifting members in said change speed transmission, an index pointer fixed on said handle, and a, U-shaped index dial fixed on said housing indicatively related to saidv index pointer on said handle.

3. In a change speed transmission having, a transmission housing, a gear set, a pair of shiftable members in said gear set, a single lever control mechanism for shifting said members comprising, an axially slidable and rockable shaft carried in the change speed transmission housing, a handle rigidly fixed on the outer end. of said shaft, a shifter spool fixed on the inner end of said shaft engaging a shifter yoke movably mounted in said housing, means for connecting said yoke to a shiftable member in said transmission, a shifter cam drum located betweensaid lever and said spool relatively axially slidable on and supported by said slidable and rockable shaft, means carried by said housing for restricting axial movement of said cam drum relative to said housing while allowing rotary movement thereof by the rocking motion of said shiftable and rockable shaft, a cam track in said cam drum, shifting lever mechanism actuated from said cam track upon rocking rotation of said handle, and means for connecting said shifter lever mechanism to shifting members in said change speed transmission, and means for limiting the outwardaxial movement of said lever by axial engagement of the spool with said cam drum.

4. In a change speed transmission having, a transmission housing, a gear set, a pair of shiftable members in said gear set, a single lever controlmechanism for shifting said memberscom prising, an axially slidable and rockableshaft carried in the change speed transmission housing, a handle rigidly fixed on the outer end of said shaft, a shifter spool fixed on the innerend of said shaft engaging a shifter yoke movably mounted in said housing, means for connecting said yoke to a shiftable member in said transmission, a shifter cam drum'located between said lever and said spool relatively axially slidable on and supported by said slidable and rockable shaft, means carried by said housing for restricting axial movement of said cam drum relative to said housing while allowing rotary movement thereof by the rocking motion of said shiftable and rockable shaft, a cam track in said cam drum, shifting lever mechanism actuated from said cam track upon rocking rotation of said handle, means for connecting said shifter lever mechanism to shifting members in said change speed transmission, an index pointer fixed on said handle, and a U-shaped index dial fixed on. said housing indicatively related to said index pointer on said handle, and means for limiting the outward axial movement of said lever by axial engagement of the spool with said cam druml RICHARD KNIGHT LE BLQNDQ nanny o. KEMPEB.

nar animons strap The following references are of record in: the

file of this patent:

UNITED STATES I ATENTS 7 Number Name Date 7 1,817,727 Hammersveld Aug. 4, 1931' FOREIGN PATENTS Number Country Date 268,456 Great Britain Oct. 4, 1926 

